Automatic turret lathe



Aug. 21, 1951 L. E. GoDr-'RlAux AUTOMATIC TURRET LATHE 12 Sheets-Sheet 1 Filed June 2, 1945 ATTORNEY Aug' 2l, 1951 E. GODFRIAUX 2,555,305

AUTOMATIC TURRET LATHE Louz'sEGod ricava IN VE TOR.

Aug- 21 1951 L. E. GoDFRlAux 2,565,305

AUTOMATIC TURRET LATHE Filed June 2, 1945 y l2 Sheets-Sheet 5 AT TORNEY,

Aug. v21, 1951 l.. E. GODFRIAUX AUTOMATIC TURRET LATHE 12 Sheets-Sheet 4 Filed June 2, 1945 frialdad INVENTOR.

` i Lx Louis E God AT TQRNEY:

Aug. 21, 1951 L. E. GODFRIAUX AUTOMATIC TURRET LATHE l2 Sheets- Sheet 5 Filed June 2; 1945 k -mmkw mmhw ZouzsE. Gaqfriaux' ATTR'NEY.

Aug. 21, i951 L. E. GODFRIA UX AUTOMATIC TURRET LATHE 12 Sheets-Sheet 6 Filed June 2, 1945 Louis EQGodfzfz'aux I IN VEN TOR ATTORNEY Aug. 2l, 1951 L. E. GODFRIAUX 2,565,305

y AUTOMATIC TURRET LATHE:`

Filed June 2, 1945 12 Sheets-Sheet 7 Louis E. Gocgf'rz'aux IN V EN TOR.

ATTORNEY.

Allg 21, 1951 l.. E. GoDFRlAUx 2,565,305

AUTOMATICTURRET LATHE Filed June 2, 1945 12 Sheets-Sheet 8 Louz'sE. Gacfzficzux l N V EN TUR.

TTORNEX Aug. 2l, 1951 l.. E. GoDFRlAUx AUTOMATIC TURRET LATI-IE l2 Sheets-Sheet 9 Filed June 2, 1945 1- INVENToIg. 2 Louzsfodfrzcmx fg? /65 B Aug. 21, 1951 L. E. GODFRIAUX AUTOMATIC TURRET LATHE 12 Sheets-Sheet lO Filed June 2, 1945 Louis E. Godfric/ux INVENTOR.

ATTORNEY,

Aug. 2l, 1951 L. E. GoDFRlAux AUTOMATIC TURRET LATI-IE 12 Sheets-Sheet 1l Filed June 2, 1945 .E .um

TTRNEY.

Aug. 2l, 1951 E. GoDFRlAUX AUTOMATIC TURRET LATHE 12 Sheets-Sheet 12 Filed June 2, 1945 ATTORNEY.

Patented Aug. 21, 1951 AUTOMATIC TURRETLATHE Louis E. Godfriaux, Madison, lWis., assigner to Gisholt Machine Company, Madison, Wis., a corporation of Wisconsin Application June 2, 1945, Serial No. 597,268

33 Claims.

This invention relates to an automatic turret lathe, and more particularly to thecontrol of the speed of the various parts during feed, and the automatic shifting of traverse and feed movements through successive cycles of operation of the lathe.

The principal object of the invention is to simplify and improve the construction of automatic turret lathes to thereby substantially reduce the cost of the same and the maintenance thereof, and provide a greater range of utility for such lathes.

Another object of the invention is to provide a turret lathe in which a greater range of speeds and feeds is provided for the several partsincluding the turret and the tool post, andinw-hich the parts may be Vfed at any rate 'within-the range of speeds provided therefor.4 i

A more specific object is to provideahydraulic control of the turret and tool post lfeeds giving a widerahge of speeds with infinite selections within the range. n A

Another object is to provide ailiighlpower'piiiiip and motor unit for feeding apart 'of "the'lathe under infinite selections `as to speed.

Another Objectis to provide a'ca'm drum on the bed of the lathe indexed with the turret and which controls the vfeeds for each cycle of operation, determines the spindle speed and initiates and terminates the lvarious feed rand traverse movements.

Other objects will appear hereinafter AVin the description of a preferred ,embodiment fof :the invention, illustrated in the accompanying drawings. n

In the drawings: l

Figure l is a side elevation of alathe embodying the invention; ,l

Fig. 2 is an end view looking at'th'e'headstock and drive;

yFig. 3 is a schematic horizontal"'section through the Aheadstock showing the hydraulic Tclutch con-- trol and gear shift mechanism;` v

Fig. 4 is a detail section taken on Lline Z4-"4 of Fig. 3 showing the high and low gear clutch actuating mechanism;

Fig. 5 is a section through the 'headstockcontrol valve showing schematically the-control connections;

Fig. A6 is a side elevation showingithe hydraulic f connections between the headstock'andthezturret carriage;

Fig. 'l is a longitudinal section Yof a telescopic connection for the hydraulic feed pipes `shown in Fig. 6;

Fig. 8 is a longitudinal vertical section through the pump and motor unit on the turret carriage;

Fig. 9 is a transverse section through the pump taken on line 9-9 of Fig. 8;

Fig. l0 is a transverse section through the motortaken on line Ill-I0 of Fig. 9;

Fig. 11 is a longitudinal section through the traverse forward and reverse clutch; f

Fig. 12 is a transverse section throughthe feed and traverse clutch taken on line I2-.I2 of Fig. 11 and showing the cam drum control;

Fig. -13 is an enlarged perspective view of a portion of `the cam drum showing the shape o f thecams and their attachment;

Fig. 14 is a detail transverse section lookingl at the forward end of the turret carriage and showing the cam drum;

Fig. l5 is a front elevation of the turret c arf riage with parts sectioned to show the control mechanism;

Fig. 1G is a transverse section taken on line I6-I6 of Fig. 1 and showing the tool post carriage and cross slide;

Fig. 17 is a rear end view of the lathe with the cover plate removed and showing the indexing mechanism for the drum and turret;

Fig. 18 is a detail horizontal section of the drum indexing mechanism taken on line lil-I8 of Fig. 17;

Fig. 19 is a detail section showing the drum index lock; and

Fig. 20 is a schematichydraulic control circuit layout for the lathe.

The lathe comprises, in general, a bed I with an oil drip pan 2 preferably above the floor level, a headstock 3, atool post 4 and a turret 5, which may be of regular standard construction for non-automatic lathes.

The headstock The headstock is driven by a motor 6 through `belt 'I and drive shaft 8. Clutch 9 is adapted to provide two different forward speeds by alter.- natively connecting the spur gears I0 and II on drive shaft 8 through the clutch to drive the intermediate shaft I2.

The high speed drive for spindle I3 is provided lby clutch I4 on shaft I2 which drives the triple -gear member I5 at the rotary speed of the shaft.

A triple gear I6 is splined to the auxiliary drive shaft Il and may be shifted longitudinally to either of three positions relative to member l5 to effect three different speeds. Lever I8 on top ofthe headstock effects shifting of gear l5.

A double gear I9 splined on shaft Il meshes 3 alternatively with gear 2u or with gear 2| on the spindle I3 to drive the latter'. The shifting of gear I9 to its alternative positions is effected by lever 22 on top of the headstock.

The low speed drive for spindle I3 is provided by small gear 23 on shaft I2 driving the large clutch housing gear 24 floating on the low-speed gear shaft 25. Y A clutch 26 effects driving of shaft 25 by the rotation of gear 24. A gear 21 on shaft 25 meshes with a drive gear 28 on triple-gear member I5.

Alternate operation of clutches I4 and 25 effects either high r low speed driving of spindle I3.

Clutches 9, I4 and 2B are operated by hydraulic cylinders in response to a master control valve 29, shown in Fig. 5.

The cylinder 30 for clutch 9 is disposed at the forward end of shaft I2 and has a piston 3I with a piston rod 32 extending axially of the shaft to engage the clutch operating lever 33.

The cylinder 34 for operating clutches I4 and 26 is disposed conveniently on the top of the headstock and has a piston 35 with a piston rod 36 having a roller 31 at its end riding in a curved recess 38 at the end of a lever 39 fixed to the vertical shaft 49. A lever 4I on the lower end of shaft 49 effects simultaneous operation of yokes 42 and 43 which in turn operate the corresponding clutches I4 and 29.

When lever 39 is pushed outwardly by piston roller 31 the yoke 43 is moved to tighten clutch 29 and yoke 42 is moved to loosen clutch i4. When lever 39 is pulled inwardly by piston roller 31 the yoke 43 is moved to loosen clutch 26 and yoke 42 is movedto tighten clutch I4.

Control valve 29 comprises a vertically disposed valve chamber having a plunger valve body 44 therein with suitable ports and passages to control the operation of the pistons 3| and 55.

The plunger 44 is moved up and down to its several positions by the rack 45 and gear 45 meshing therewith. A spring 41 forces the plunger 44 upwardly against the top of the valve cylinder and gear 45 operates against the spring to move plunger 44 downwardly to its several operative positions.

The hydraulic connections through the valve are from pump 48 to intake port 49, through the valve and respective cylinders and returning by discharge port 59 and conduit to sump 5I.

As shown in Fig. the pressure fluid entering the valve through port 49 passes upwardly around .the plunger 44 to port 52 from where it is conducted to the right-hand end of cylinder 34. Fluid is exhausted from the left-hand end of cylinder 34 to port 53 in valve 29 and from thence through passage 54 in plunger 44 to the lower end of the valve chamber and out through port 59 to the sump 5I.

v The piston 35 is held to the left in Fig. 5, thereby tightening clutch I4 to provide a high speed drive for spindle I3.

At the same time pressure fluid is conducted from port 49 through passage 55 in plunger 44 to the port 5S leading to the right-hand end of cylinder 3D to effect a drive connection through vgear I9 to shaft I2. Fluid is exhausted from the left-hand end of cylinder 38 to port 51 and thence through port 5I) to sump 5I By moving plunger 44 downwardly from the position shown, until flange 58 thereon passes port 51 and flange 59 passes port 59, the fluid pressure is reversed in cylinder 3U, while cylinder 34 with its piston remains the same as before.

In this new position fluid pressure passes from port 49 through passage 55 to port 51 and into the left-hand end of cylinder 39 to effect a drive connection through gear II to shaft i2. Fluid is exhausted from the right-hand end of cylinder 3D to port 55 and thence through passage 54 to discharge port 59 and sump 5I.

Movement of plunger 44 downwardly to the next position causes flange 59 to move to below port 51, and the next flange 5U moves to a location between ports 56 and 51. Flanges 6I and 52 are disposed between ports 53 and 55. Top flange 53 is disposed between ports 49 and 52.

In this position the pistons in both cylinders 39 and 34 are reversed. Fluid pressure passes from port 49 directly through lport 53 to the lefthand end of cylinder 34, thereby moving lever 39 to the right, releasing clutch I4 and tightening clutch 2'3 to provide a low-speed for spindle I3. Fluid is exhausted from the right-hand end of cylinder 94 through port 52, passage 54 and port 59 to the sump 5I.

At the saine time pressure fluid passes from port 49 through passage 55 and through port 5G to the right-hand end of cylinder 39. rIhis effects movement of piston 3| to the left and operation of clutch 9 to drive shaft I2 by gear IU on .shaft 8. Fluid is exhausted from the left-hand end of cylinder 39 through port 51, passage 54 and port 59 to sump 5 I.

Movement of plunger 44 downwardly to its next and lowermost position reverses cylinder 30 and clutch 9 while retaining cylinder 34 and clutches I4 and 28 in the position just described.

In the lower position of plunger 44 pressure fluid passes from port 49 through passage 55 to port 51 and thence to the left-hand end of cylinder 30 where it moves piston 3l to the right and effects operation of clutch 9 to drive shaft I2 by gear II on shaft 8. Fluid is exhausted from the right-hand end of cylinder 39 through port 55, passage 54 and port 5U to sump 5I.

The valve 29 has been described as having four different positions effecting Operation of clutches 9, I4 and 26 to produce different speeds for spindle I3. In the first position of plunger 44 shown in Fig. 5, the spindle is driven through high speed gear i9, clutch 9, high speed clutch I4, gears I5 and I5, gear I9 and either gear 20 or 2I. In the second position described the spindle is driven through low speed gear II, clutch 9, high speed clutch I4, gears I5 and I5, gear I9 and either gear 20 or 2I. In the third position described the spindle is driven through high speed gear IIJ, clutch 9, gears 23 and 24, low speed clutch'26, gears 21 and 28, gears I5 and I5, gear I9 and either gear 29 or 2|. In the fourth position described the spindle is driven through low speed gear I I, clutch 9, gears 23 and 24, low speed clutch 26, gears 21 and 28, gears I5 and I6, gear I9 and either gear 20 or 2|.

The pump 48 is driven by belt 64 from an auxiliary pulley 65 on the outer end of shaft 9.

Three shafts extend the length of the lathe in front of the bed. Shaft 65 carries gear 46 for operating valve 29 and extends through the turret carriage 61 where it is rotated by suitable control mechanism hereinafter described.

The traverse shaft 68 is driven by suitable belt connections 69 from pulley 55 on shaft 8.

The feed shaft 10 for transmitting feed movement to carriage 51 is driven by chain 1I from the spindle I3.

Turret carriage drive The feed of the turret carriage by feed shaft is effected by means of a rotary pump-motor unit of high torque and infinitely variable speed within the range of speeds required. A suitable pump-motor combination Vis illustrated in' Figures 8, y9 and 10.

The pump l2 is driven by a sprocket 13 on pump shaft 1,4, and a chain 'l5 from sprocket'l sliding on and keyed to rotate with `feed shaft 10. Sprocket 16 is journaled in the carriage 61 and is adapted to move axially along shaft I with the carriage 6l. The rotation of the pump shaft 14 is thus correlated with and determined bythe speed of spindle I3.

vThe pump 72 receives pressureuid from pump 48 through conduit Tl extending along the front of bed I as shown in Figures 1 and 5. A suitable telescopic connection 'I8 illustrated in detail'in Fig. 7 is provided in conduit Il to provide for the movement of the pump`l2 with turret carriage '6l toward and away from the headstock 3 and pump 48.

The pump 12 is mounted on the front of turret carriagel and is preferably of the 'type set forth in applicants copending application Serial No. 554,884, filed September 20, 1944, now Patent No. 2,444,159, granted June 29, 1948, for Fluid Pump.

The pump 12 comprises a plurality of adiacent cylinders 'I9 in which individual pistons 8S' are operated by eccentric cam rings 8l on the rotary tubular pump shaft 74. The pistons 85 are biased upwardly by coil springs 82 in the respective cylinders to engage the cam rings 8|.

The cam rings 3| are mounted for adjustment eccentrically of shaft 14 by radially extending supports 83, there being a pair of such supports for yeach ring. The supports 83 extend through the wall of the shaft 74 and engage longitudinally movable cam blocks 84 within the shaft and which hold the corresponding pairs of supports 83 in any desired position relative to the axis of the shaft 14.

Adjustment of blocks 84 axially of the shaft Mis effected by means of a push rod 85 in the outer end of the shaft and by the springs 89 between the blocks and the rear end spring 8l biasing the blocks outwardly against the push rod. Each block 84 has an axially movable central pin 188 with a head 89 against which the adjoining spring 81 or 86, as the case may be, presses to facilitate holding of the blocks in place and individual adjustment of the same as more fully explained in the copending application referred For any given speed of spindle i3 the pump shaft 14 rotates at a constant speed and effects a given number of strokes of pistons 88 per unit of time. The volume of pressure fluid pumped, however, varies with the stroke of the pistons 80, and the latter is dependent upon the eccentricity of the cam rings 8| on shaft 74.

By pressing push rod 85 inwardly to the position shown in Fig. 8 and beyond the eccentrcity ofthe cam rings 8| can be increased resulting in a corresponding increase in the stroke of pistons 80 and the volume of uid pumped.4

By releasing push rod 85 for outward movement under the influence of the biasing springs 86 and 87, the eccentricity of the cam rings 8| can be reduced resulting in a corresponding decrease in the stroke of pistons 8E) and the volume of fluid pumped. y

IThe regulation of the volume of fluid pumped,

6 by means of push rod can be effected at any time and to any extent during operation of the' pump and with substantial accuracy.

The motor 98 is constructed in the same housing as pump 12 and is operated by the fluid pressure from the pump. 'I'he motor Si) is preferably of the general type set forth in the copending application of the present inventor, Serial No. 554,883, filed September 20, 1944, now Patent No. 2,471,484, granted May 3l, 1949, for Hydraulic Motor.

The motor 96 has its shaft 9| aligned-with pump shaft 'M and spring 81 is disposed axially in the hollow shaft 9| to save in space and at the same time provide a long spring of the desired characteristics for operation of the pump. A suitable thrust bearing 92 is provided between spring 3i and the innermost block -84 to take up the differential rotary speeds of the two.

The motor 99 comprises, in general, a plurality of cylinders 93, each containing a piston 94 having a roller 95 engaging a cam member 95 on the shaft 9| to drive the latter'.

The cam members 96 are radially disposed at different angles spaced around the axis of shaft 9| so that the pistons 94 have their corresponding operating strokes in succession to prov-ide a substantially continuous drive for the shaft.

Each cam 95 is designed -to deliver a uniform rotary torque to shaft 9i proportional to the movement of the corresponding piston during its working stroke. n other words, each increment of upward movement cf a piston 94 in vits working stroke effects a corresponding increment of rotation of the shaft 9|. Equal increments of movement of a piston 94 in its working stroke effect equal increments of rotation of the shaft.

The distribution of power duid from pump l2 to the respective cylinders 93 of motor 98 is timed by a suitable distributor ai geared to motor shaft Sl.

The exhaust of the motor 99 is returned to sump 5| through conduit i8 which extends parallel to and adjacent the pressure conduit il and is similarly constructed.

The speed of motor 99 is dependent upon the volume of liquid pumped by pump l2. The pump l2, being adapted to deliver a predetermined variable quantity of liquid, readily controls the speed of the motor.

The employment of the particular pumpmotor unit described has considerable advantage in lathe operations, since it provides an infinite and accurate adjustment of speeds over a wide range and is practically non-stalling. The motor will deliver a substantial torque throughout a wide range of speeds varying from only a fraction of a revolution per minute to over one hundred revolutions per minute.

The motor shaft 5| has a worm gear 99 secured thereon for driving a tubular clutch member |80 mounted to rotate freely on the feed clutch shaft fill extending transversely of the carriage 6l. A second clutch member |51?. is keyed to shaft IU! and has an intermediate axially movable clutch member |83 interlocked for rotating the same and adapted to abut the end of member |89 under the .biasing iniiuence of springs |94. The abutting ends of ciutch members ID3 and |83 are toothed to provide a feed clutch so that when they are engaged they eifect driving of the shaft lill by worm gear 99.

Shaft IBI has a pinion |95 on its inner end meshing with a gear rack |89 extending longitudinaiiy on the "underside of a aange on bed l of the lathe, so that rotation of shaft effects movement of the carriage 61 along the bed. The speed of the feeding movement of carriage 61 is dependent directly upon the speed of motor 00 which in turn depends basically upon the speed of spindle I3 and is controlled or modified by the push rod 85.

Clutch member1 |03 is pushed axially against springs |64 and out of engagement -with the constantly rotating clutch member |00 by means of a piston |01 in a cylinder |08 at the outer end of the housing for shaft |0I. The piston |01 carries a rotatable piston rod |09 extending axially into the end of the shaft |0I and which is adapted to abut against a cross member ||0 riding in a slot I in the shaft and in turn f1tting into recesses in the clutch member |03.

A conduit ||2 supplies pressure fluid to cylinder |08 from a suitable control valve hereinafter described and which receives pressure fluid through conduit 11 from pump 48, to move the piston |01 inwardly in a direction releasing the clutch |03. When the pressure on the piston in cylinder |68 is released and the conduit |I2 connected to the sump the springs |04 move clutch |03 into engagement with member |00 and effect driving of shaft |0| by motor 90.

The traverse drive for carriage 31 is effected through a forward and reverse clutch mechanism from the constantly rotating traverse shaft 68, as shown in Fig. 11.

The axially spaced forward and reverse beveled ring gears I I3 and ||4 are rotatably mounted on a sleeve ||5 splined to shaft 68. The gears ||3 and I I4 mesh with the opposite sides of a beveled gear ||6 secured to the lower end of vertical shaft I |1. A worm gear I |8 secured to the upper end of shaft ||1 drives gear ||9 and feed shaft |0| to drive the carriage 61 in traverse.

A central clutch member is keyed to sleeve ||5 for rotation therewith and axial movement thereon. The member |20 is adapted to clutch ring gear I|3 when moved axially toward the same to drive the gear from shaft 68. wise, when member |20 is moved axially in the opposite direction it releases ring gear ||3 and clutches with ring gear ||4 to drive the latter from shaft 68.

The alternate clutching of ring gears ||3 and ||4 effects the respective forward and reverse traverse drive for the carriage 61 through beveled shaft |0I and pinion |05.

Control of clutch |20 is provided by the lever I2I having its upper end pivoted at |22 to the clutch housing and extending as a yoke riding in a circumferential groove in member |20. The lower end of lever I2I extends between two opposed pistons |23 and |24 in the corresponding cylinders and |26.

Conduits |21 and |28 connect to the ends of the corresponding cylinders |25 and |26 to su'pply pressure fluid thereto for operating the respective pistons |23 and |24.

When conduit |21 is connected to pump 48 through conduit 11 and a suitable valve hereinafter described to supply pressure fluid behind piston |23 in cylinder |25, conduit |28 is connected through the valve referred to and conduit 9S to drain fluid from cylinder |26 to sump 5|.

This results in movement of lever |2| to the right and engagement of clutch |20 with gear |4 to drive the same from shaft 68.

When conduit |28 is connected to pump 48 through the valve referred to and conduit 11 to supply pressure uid behind piston |24 in cylinder |26, conduit |21 is connected to drain fluid from cylinder |25 through the valve referred to and conduit 98 to sump 5|. This results in movement of lever I2I to the left and engagement of clutch |20 with gear ||3 to drive the same from shaft 68.

The control valve |29 for controlling the supply of pressure fluid to cylinders |08, |25 and |26 is shown in Fig. 15.

The control valve |29 is of the piston type and comprises a valve body |30 having a cylindrical main valve chamber |3| with a central inlet port |32 for pressure fluid from pump 48 and an end discharge port |33 for fluid return to sump 5|, and a cylindrical routing Valve chamber |34 with three longitudinally spaced ports |35, |36 and |31 in its side.

Port |35 connects with conduit |21 leading to cylinder |25, port |36 connects with conduit |I2 leading to cylinder |08. and port |31 connects with conduit |28 leading to cylinder |26.

The chambers |3| and |34 are disposed side by side and have two longitudinally spaced ports |38 and |39 connecting the same through the common side wall thereof.

A main valve plunger |40 is reciprocably disposed in chamber |3| and has four flanges fitting the inside Walls of the chamber and providing a wide central circumferential inlet groove |4| and two end circumferential discharge grooves |42 and |43, respectively. The discharge grooves |42 and |43 are connected by ports |44 to a longitudinal passage |45 in plunger |40 and which opens to the right-hand end of chamber |3| from which port |33 drains to the sump 5| through conduit 98.

When plunger |40 is in its central position, as shown in Fig. 15, which is the feed position for carriage 61, the central groove I4| is closed, and ports |38 and |33 communicate with the corresponding grooves |42 and |43 and effect discharge into sump 5| from both ends of routing valve chamber |34.

When plunger |40 is moved to the left, to back traverse position, the central groove |4| connects inlet port |32 with port |38 to supply pressure fluid to the left-hand end of chamber |34, and at the same time end groove |43 connects port |39 to the discharge port |33 and sump 5|.

When plunger |40 is moved to the right, to the forward traverse position, the central groove |4| connects inlet port |32 with port |39 to supply pressure uid to the right-hand end of chamber |34, and at the same time end groove |42 connects port |38 to the discharge port |33 and sump 5I The routing valve plunger |46 has a central piston member |41 tting in the valve chamber |34 between ports |38 and |39 to serve as the motivating means for reciprocating the plunger under the influence of the pressure fluid admitted through either port |38 and |39.

When pressure fluid is admitted to chamber |34 through port |38 it forces piston |41 to the right until it uncovers the ports |35 and |36 to expose the same to the pressure fluid through port |38. The end of the plunger |46 engages the end of chamber |34 and limits the movement of piston |41 to the right, thereby retaining an open connection for drainage of fluid from cylinder |26 through conduit |28, port |31, port |39, and port |33 to sump 5I.

In this latter position of piston |41 pressure luidisadmitted to cylinder |08 through ports |38-candv |36 and conduit 2, thereby opening clutch-.l 03 todisconnect motor-90 from feed shaft |I. At the same time pressure fluid is admitted to cylinder through ports |38Yand |35 and conduit |21 to push piston |23 and move lever |2| to the. right, thereby effecting back traverse drive for carriage 61 through gear ||4.

When pressure fluid is admitted tochamber |34 through port |39 it forces piston |41 to the left until itA uncovers the ports |36. and |31 to expose the same to the pressure fluid through port |39. The endl of 'plunger |46 engages the endA ofchamber |34l and limitsl the movement of piston |41 to the left, thereby retaining an open connection fory drainage of fluid from cylinder |25f-through conduit |21, port |35, port |38 and port- |33 to sump 5|.

In thislatter. position of piston |41 pressure fluid is admitted' to cylinder |08 through ports; |36 andlif and conduit I2, thereby opening clutch |.03f-to disconnectV motor 06 from feed shaft |6|. At the same time pressure fluidA is admitted to cylinder |26' throughports |39 and |31 and conduit |28 to push-piston |24 and move lever |2| to the left, thereby effecting forward traverse drive for carriage 61 through gear I3.

When the mainsvalve plunger |00 is. moved to central position to cut off pressure fluid from both ports |33 and, |39, as shown in Fig. 15, the f ports |38y and |30 registery with the correspondinggrooves |42- and |43 and serve to connect. all of the cylinders. |08, |25 and |26 to sump 5|, thereby allowing .clutch |03 to engage member |00 and veffect-feeding of carriage 61 by motor 95, whilelever' |2I drops to central position where both the forward andA reverse clutches are open.

The main plunger |40 is operatedY by an axial piston rod 48Y extending. through the end of valve body- |30'. A manna-liever.` arm |45'is secured on the front` of theh carriage 61' adjacent valve |28 and turns ashaft |50 having an upwardly extendingV forked arm |5| engaging a cross pin |52 in the outer end of rod |48 to operate the latter.

Since'thecylinders |25 and |26 are below the level of sump 5| and of control valve |29, a small scavenger pump |53 is provided in the housing for the forward and back traverse clutch and is operated vby an eccentric |54 on the sleeve H5: to

facilitate the return of uid from the cylinders to thesump.

The automatic control mechanism The automatic control of the various movements, including4 the spindle speed, traverse and feed of the turret carriage an'd the traverse and feed of the tool post, is provided by a camdrum |55` mounted on'the front of bed and extending .longitudinally betweenv a forward, bracket 56 near the tool post carriage |51 and the rear end housing |58 for the indexing mechanism.

The rkcam drum |55 extends longitudinally adjacent the path of movement of carriage 61 and has` six sidesl corresponding to the six sides of turret 5vrwhich is mounted on the carriage. Each side of the drum |55 has a set of cam strips and stops .for controlling all of the lathe operations necessary for performing the machining opera tions. corresponding to the tools on the particular face of the turret 5; both the turret 5 .and the drum |55. being indexed simultaneously and in direct correlation-with each other.

Referring to. a single face. of the cam drum |55, there are-two grooves |56 and |60 extending longitudinally of the drum and in which the sev eral cam strips and stops are adjustably secured by split expansion clamps |61, as shown in Fig; 13.

A wiper cam trip |62 isfsecured near the rear end of the drum for engaging aldepending projection |63 on afplate |64 secured to shaft- |50' to turn the latter and lever |49 vtoforward traverse position as the cam drum. |55 turns'- to index the particular face..

AS the carriage 6-1 moves forwardly: in traverse, a cam follower |65 engages and rides on top of a cam strip |66 clamped against the forward side of groove and which has. a predetermined height.

The cam follower |55vsupports a vertical. rack |61 which operates a. cross* rack'` li'bypinion |60. The cross rackv |68 meshes with a pinion |10 on shaft 66 which operates the control-valve 29 at the front of the headstock 3' to: set andi vmaintain the spindle speed as'represented by the height of cam strip |66.

The cam |1| clampedagainst the back side of groove |60 has an offset lip-which engages the rear descending projection |12 on plate |64 to swing shaft |50 and lever'l49v to. center feedposition as the carriage reaches.` the position for stopping the forwardA traverse'and commencing the forward feed. Fromi that point *on' thefcarriage 61'moves forward at the predeterminedfeed rate.

When the carriagerreaches'the forward end of its feed a second cam |13 offsetin thefopposite direction from cam |1'| abuts against the projection |63to swing the shaft |50andlever |49`to back traverse position. As. thecarriage returns rearwardly in back traverse movement projection |63 on plate |64 misses the oifset'cam v|1|, since projection is lateraly offsetfrom projection |12, asV shown in the drawing;

The rate'offeed for carriage 61 is primarily determined by the spindle speed as previously described, and secondarily determined by thev vol'- ume of pressure fluid supplied to motor 00 from pump 12: as regulatedby the push rod `85.

The position of push rod during feeding of the` carriage is Vdetermined and regulated bycam strip |14 clamped against' the front side of groove |50 and upon which the camfollower |15 rides.

The'cam follower |15, when riding on strip |14 supports the vertical rack |16-'which meshes with a gear |11 rotatably mounted on apivot shaft The other side-of the gear |11 diametrically opposite the rack |16 meshes with a gear segment |18 on a rocker arm |80 carried by a rock. shaft |84 journaled in a bracket |82 on the. forward end of the housing for pump 12.

A second rocker arm |83 integralwith the .rock shaft |8| extends upwardly and carries. at its end an adjustable abutment screw. |84 threaded therethrough and axially pressing against the push rodl 85.

The higher cam strip |14is, the farther'will abutment |84.push the. rod 85inwardly of the pump and the greater will be the volume of rpressure fluid supplied to the motor 90.

The cam strip |85 clampedagainst the back lof groove |59 controls the feed for-the tool post 4.

In the present embodiment the tool post 4.is mounted on a cross slide |86 which inturn is mounted on the tool post carriage |51, and cam strip |85 controls the feedpf the crossslide.

Af. followerH |81 rides on strip |85 andgrad ll ually raises a vertical rack |88 meshing with a gear segment |89 having trunnions |90 journaled in bearings |9| in the bottom of the housing for pump 12.

A second gear segment |92 diametrically opposite segment |89 and disposed on a longer arm |93, meshes with a gear |94 keyed upon shaft |95 to rotateY the latter.

The shaft |95 is journaled in carriage 61 and extends forwardly through the tool post carriage |51 where it slides through a sprocket |96 which is keyed to it to rotate therewith.

A chain |91 drives a sprocket |98 on the tool post carriage |51 from sprocket |96 on shaft |95. The sprocket |98 in turning in one direction drives the plunger of control valve |99 for admitting pressure fluid to one end of power cylinder 200 to feed cross slide |86 inwardly. Turning of the sprocket |98 in the opposite direction drives the control valve plunger in the opposite direction for admittingpressure huid to the opposite end of power cylinder 200 and gradually withdraws the cross slide. The pressure fluid for operating power cylinder 200 is supplied by conduit 11 through take-off block 20| and is similarly returned to the sump by conduit 98.

Various types of drive may be provided for feeding cross slide |86. It is preferred to employ a servo-motor construction for valve |99 and power cylinder 200, such as that set forth in copending application Serial No. 608,985, filed August 4, 1945, by the present inventor.

The longitudinal movement of the tool post carriage |51 is also controlled by drum |55. For this purpose a segmented cam ring 202 is provided on the right hand end of drum |55 for engaging the lever arm 203 of a limit switch 204.

When a segment of ring 202 raises the arm 203 the switch is operated to effect operation of the solenoid cross-over valve 205 which controls the supply of pressure fluid from pump i8 to a cylinder 205 secured to the front of the headstock 3.

A piston 201 in cylinder 206 has a rod 208 exirding longitudinally and secured to the carriage When the switch arm 203 is raised by cam ring 202, the valve 205 is operated to admit pressure fluid to the left end of cylinder 206 and to exhaust fluid from the right end of the cylinder, thereby moving carriage |51 to the right until an adjustable stop 209 locates it for operation of the cross slide.

When the switch arm 203 is allowed to fall, the valve 295 is operated to admit pressure uid to the right end of cylinder 206 and to exhaust uid from the left end of the cylinder, thereby moving carriage |51 to the left until the piston 201 reaches the end of the cylinder.

The segments of the cam ring 202 will be disposed to actuate switch arm 203 to retract the tool post carriage at such times as the tool post should remain inactive, as for instance during loading and unloading of the lathe or during machining operations by the turret corresponding to a particular face of the cam drum |55 where tool post machining is not to be employed. In all other positions the switch 204 effects forward positioning of the carriage where the tool post can be employed.

A second limit switch 2|0 constitutes the stop button for the lathe and automatically controls the stopping of motor 6.

The switch 2|0 is located adjacent switch 204 and has an arm 2| I actuated by a button 2|2 on l 2 drum |55 to stop motor 6 when the complete machining cycle is finished and the drum |55 is indexing to a starting position for the next succeeding machining cycle.

A manual start and emergency stop switch 2 |3 is provided on the front of headstock 3. In addition, an emergency stop manually operable bypass valve 2|4 for stopping the feed of the carriage 61 is provided on the front of the carriage.

Turret and control drum indexing The mechanism for indexing the turret 5 and the cam drum |55 is disposed in the index housing |58 at the rear end of the bed and comprises, in general, a normally open clutch tripped to closed position by the rearward return of carriage 61 and adapted to effect a predetermined simultaneous rotation of the turret and of cam drum from the constantly rotating traverse shaft 68 to present the next working face of the turret and the corresponding control face of the drum.

Various types of clutches may be employed, the clutch illustrated comprising a beveled gear 2|5 freely rotating on a transverse shaft 2 |6 and driven by a gear 2 |1 on the rear end of traverse shaft 68, an axially movable clutch member 2|8 keyed on shaft 2|6 and adapted to move toward gear 2|5 and effect a positive interlock with a spring backed pin 2|9 extending from the face of the body of the gear and which enters a recess 220 in the face of the clutch member 2| 8. to drive the shaft 2|6 from gear 2|5.

The mechanism for moving the clutch 2 I8 into engagement comprises a bell crank lever 22| pivoted on a vertical stud 222 secured in the bottom of housing |58. One arm of the lever 22| extends at right angles to the shaft 2|6 beneath the same and has an upwardly extending pin 223 at its end riding in a circumferential groove 224 in clutch member 218. The other arm of lever 22| extends to the left in Figs. 17 and 18 and has pivotally secured thereto a pusher arm 225 normally extending forwardly of the lathe in alignment with a hole 226 through the front wall of housing |58.

A trip pin 221 is carried by carriage 61 in line with hole 226 and is adapted to move axially against a holding spring 228 on the carriage to allow the carriage to continue in its rearward traverse movement after pin 221 engages pusher arm 225.

The engagement of pusher arm 225 by pin 221 as the latter comes through hole 226 effects operation of the bell crank lever 22| in a direction causing closing of the clutch 2|8 and driving of shaft 2|6 by gear 2|5.

The shaft 2|6 effects rotation of the turret 5 for indexing the latter by means of the beveled gear 229 at the right end of the shaft driving vertical shaft 230 which in turn is geared to drive the turret index shaft 23|.

The shaft 2|6 also effects rotation of drum |55 for indexing the latter by means of the worm gear 232 at the left end of the shaft meshing with gear 233 on the end of a stub shaft 234 supporting the drum.

When the turret 5 and drum |55 have been rotated to their next working position the clutch 2|8 is disengaged by a trip mechanism comprising a wheel 235 on shaft 234 and having a dog 236 secured thereon for engaging an adjustable screw 231 in a hanging post 238 to swing the latter against pusher arm 225 thereby releasing the latter from the end pressure of pin 221.

Spring 239 then returns bell crank lever" 22| to its normal positiony opening theclutch'.

The smalllateral movement of pusher arm 225 under pressure from post. 238 for releasing pin 221, is. provided by a lost motion'pivotal connection between arm 225 and the end of bell crank lever 22| A spring 240 retains the pusher arm 225 in `normal alignment with pin 221.

Where the drum and turret are to be indexed at' each successive face there will. be a dog 236 disposed on wheel 235 for each face. In case' it is desired to skip one or more working faces', the dog or dogs corresponding to the same are removed, thereby allowing the clutchy to continue closed and to rotate the shaft 2|6 until a dog 235 engages contact 231 and trips the clutch disengaging mechanism. In this event the wiper cam |62 corresponding to the omitted dog 236 is also omitted to avoid tripping lever |49 to forward traverse position as the drum |55 passes the index position.,

A lo-st motion connection is provided between drum. |55 and shaft 234 by means.k of a loose key 24|.

A spring-backed locking; pin 242 is disposed in acylinder 243 attached to the front side of housing |58 and is directed radially toward the end member 244 of drum |55.

Member 2414! hasa series of angular recesses 245 thereinr which are accurately located relative tothe corresponding-faces of the drum so that when pin 242 enters a given recess it locks the drum in position for the corresponding face to be operative in controlling the cycle of the lathe.

The shape of the recesses 245 is such that when pin 242 starts into a recess it gives a quick. forward rotary acceleration to the drum which effects positive location of pin 242 at the bottom of the recess and accurate indexing and in addition effectsA a quick wiping action of trip |62I past' projection |63 to start the forward traverse of car'- riage-61.

Where a stop rod 246 is employed. forl turret carriage 51, it is indexed, alongl with; theturret 5-and control drum |55 byv means ofchain 241 driven from sprocket 248 on shaft-234..

Operation of the lathe summarizing the operation of the lathe, when a blank has been chucked on the end of spindle I3 switch button 2|3 is pushed to start motor which drives headstock t,r traverse shaft 68,V feed lshaft wand pump 48.

The lever |49 is either in forward traverse-position, by reason of the wiping action of cam |62 upon the last indexing of drum |55, or it. can be manually moved to forward traverse position', and the forward traverse clutch drives carriage 61 forwardly.

WhenV cam follower ,l 66V engages. andf rides, upon cam strip |56 the plunger 44' for control valve 29 is operated to shift clutches. 9, |4- and. 26 in headstocky 3 to provide the required speed` for spindle |3.

When.. the* carriage. reaches'. the-r position for commencement of its. forward. feedcam. |.1| on drum |55engages. dog |12`to swing leverf|49 to feed position, thereby disengagi'ng' the'forward tra-verse clutch` andI engaging the feed `clutch |03 toyeffectfeed of the carriage at a: rate determined bythe spindle speed and by the additional superimposed control ofpump 12.'.andmotor 96.1

Follower |315.1 riding orrcam strip |14: effects afcontinuous control of thedi'splacement of pump 14.' 12 as the carriage 61 moves forwardly driven by motor 96.

In the meantime, limit switch 264 is moved by cam segment 252 to operate solenoid valve 205 and effect longitudinal movement of the tool post carriage |51 to its rear position. As carriage 61 moves forwardly, follower |81 rides slowly'upwardly on cam |55 to regulate the servomotor on carriage |51 and feed the cross slide |86 and its. tool post 4. to the work.

When the carriage 61 reaches the forward end of its intended feed, the cam` |13 abuts dog |53 and trips lever. |45 to back traverse position, engaging the back traverse clutch and disengaging feed clutch |63.

The carriage 61 continues in its back, traverse movement until dog |63 engages a radially extending cam portion of wiper cam |62 and is lifted thereby to swing lever to feed position. At this time pin 221 engages pusher arm 225 and caus-es the clutch member ZIB to Aengage and effect indexing of turret 5 and drum |55to the next face, whereuponthe next successive wiper cam |62. on drum trips lever |59 to forward traverse position for the carriage 61.

When all of the operations have been completed and the work piece is to be removed, the button, 2|2.- operates limit switch ZIB to stop-the lathe.

The complete cycleof operation ofthe lathe involves loading, starting the main motor and the forward traverse of the turret carriagefollowed byv forward feed and .final back traversev corresponding to the first indexed position of the turret, the indexing of the turret and of the cam control drum to each succeeding working posi.- tion followed in each instance by the forward traverse, feed and back traverse of the. carriage until alll of the machining operations have been completed, stopping of the main motor, and unloading. The cycle further involves the moving of the tool post carriage to and from position and each indexed position of the turret calls for the setting of the spindle speed,. the control of the turret carriage feed, and the control. ofthe tool post cross slide feed.

The invention provides many features of advantage in the construction of an automatic turret lathe. The employment of a pump-motor unit of the class described for feeding the carriage or any other tool. supporting member provides a, wide range of speeds from a very slow speed up to a maximum without variations in torque for a given load. It also provides. a simple and easily maintainedmechanism for varying the feed rate in correlation with the carriage movement.

The'employment of a vrotary hydraulic motor for feeding purposes provides a smoother and more constant feedingmotion and better eliminates any tendency to chatter as in the case of large single pistons employedY for feeding operations, particularly where a considerable amount ofpower is required overal long movement-as in the feeding of a turret carriage.

The employment of a master control drum mounted on the bed instead of on the carriage and interengagingwith members on the moving carriage permit-s the use of a longer drum with more accurate cams and adjustable placement of the cams longitudinally of the drum for instantaneous control of each function of the lathe in accurate correlation with the movement and position ofthe carriage at all times.

The employment of a single hydraulic power system for carrying out the several control functions greatly simplifies the control and enables the employment of individual cam members to control each function in proper correlation and sequence and without interfering with any of the other functions. fi

rElie employment of an indexing mechanism in the rear end housing provides an accurate common index for the turret, the Control drum and the stop rod, and locates the mechanism for ready repair and maintenance.

. Various embodiments of the several features of the invention may be employed Within the scope of the accompanying claims.

I claim:

l. In a lathe or the like, a tool carrying member requiring feeding movement over a substantial length of travel at a selected speed within a wide range of speeds in which the maximum speed is in excess of one hundred times the minimum speed, a hydraulic positive displacement motor disposed to drive the member at any selected speed throughout the range of speeds by variation in speed of the motor, said motor comprising a motor shaft, a plurality of cylinders with corresponding pistons for successively transmitting torque to said shaft, and cam members on the shaft disposed to translate the reciprocal movement of the pistons into a substantially constant rotary movement of the shaft with substantially equal increments of rotation of the shaft for corresponding equal increments of movement of each of the pistons in the respective power strokes thereof, and said motor having a uniform torque output for a selected uniform throughput of power liquid and being governed in speed by the volume of power liquid passing therethrough, means to feed said member from said motor shaft, separate alternative means to traverse said member forward and back and means disposed to selectively vary and constantly control the volume of power liquid supplied to said motor in correlation to the travel of said tool member.

2*. In a lathe or the like, a tool carrying member requiring feeding movement over a substantial length of travel at a selected speed within a wide range of speeds in which the maximum speed is in excess of one hundred times the minimum speed, means to traverse said members forward and backward, a motor-pump unit for driving the member at feed and semi-traverse rates and comprising, a rotary motor shaft disposed to drive the member, a plurality of cylinders with corresponding pistons for successively transmitting torque to said shaft, cam members on the shaft disposed to translate the reciprocal movement of the pistons into rotary movement of the shaft with substantially equal increments of rotation of the shaft for corresponding equal increments of movement of each of the pistons in the respective power strokes thereof, said motor having a uniform torque output for a selecteduniform throughput of power liquid and being governed in speed by the volume of power liquid passing therethrough, a variable displacement pump adapted to deliver to said motor a selected volume of power liquid, and means to regulate the displacement of said pump to select and regulate the speed for said member in correlation to the travel of the tool member'.

3. In a lathe or the like, a tool carrying member requiring feeding movement at a selected speed Within a Wide range of speeds in which the maximum speed is in excess of one hundred 16 times the minimum speed, and a motor-pump unit carried by said member for driving the same and comprising, a rotary motor shaft disposed to drive the member, a plurality of cylinders with corresponding pistons for successively transmitting torque to said shaft, cam members on the shaft for translating the reciprocal movement of the pistons into rotary movement of the shaft With substantially equal increments of rotation of the shaft for corresponding equal increments of movement of each of the pistons in the respective power strokes thereof, a variable displacement pump adapted to deliver to said motor a selected volume of power liquid, means to supply liquid under a substantially constant initial pressure to said pump, and cam means coordinated with the movement of said member and disposed to regulate the displacement of said pump and thereby select the speed for said member.

4. In a lathe or the like, a tool carrying member requiring feeding movement at a selected speed Within a wide range of speeds in which the maximum speed is in excess of one hundred times the minimum speed, and a motor-pump unit for driving the same and comprising, a rotary motor shaft disposed to drive the member, a plurality of cylinders With corresponding pistons for successively transmitting torque to said shaft, cam members on the shaft for translating the reciprocal movement of the pistons into rotary movement of the shaft, a rotary pump shaft, a plurality of adjustable cam members secured on said shaft, a plurality of pistons driven by corresponding cams on said shaft and operating in individual cylinders for pumping pressure iiuid to said motor, means to drive said pump shaft at a predetermined speed, and means correlated with the advance of said tool carrying member and disposed to adjust said cams on said pump shaft and thereby determine the displacement of said pump to select the speed for said member.

5. In a lathe or the like, a tool carrying member requiring feeding movement at a selected speed within a Wide range of speeds in which the maximum speed is in excess of one hundred times the minimum speed, and a motor-pump unit carried by said member for driving the same and comprising, a rotary motor shaft disposed to drive the member, a plurality of cylinders with corresponding pistons for successively transmitting torque to said shaft, cam members on the shaft for translating the reciprocal movement of the pistons into rotary movement of the shaft, a rotary pump shaft, a plurality of adjustable cam members secured on said shaft, a plurality of pistons driven by corresponding cams on said shaft and operating in individual cylinders for pumping pressure fiuid to said motor, and means correlated with the advance of said tool carrying member and disposed to adjust said cams on said pump shaft and thereby determine the displacement of said pump to select the speed for said member.

6. In a lathe or the like, a headstock having a rotary spindle, a tool carrying member requiring feeding movement at a selected speed within a wide range of speeds, and a motor pump-unit for driving the same and comprising, a rotary motor shaft disposed to drive the member, a plurality of cylinders with corresponding pistons for successively transmitting torque to said shaft, cam members on the shaft for translating the reciprocal movement of the pistons into 

